ES2365479T3 - SIDE CHANNEL COMPRESSOR. - Google Patents

Abstract

The invention concerns a side channel compressor for compressing a gas, the side channel compressor comprising a housing (3), a side channel (30) located in the housing (3) for compressing a gas, a gas inlet opening which is formed in the housing (3) and is in flow connection with the side channel (30) for introducing a gas to be compressed, a gas outlet opening (32) formed in the housing (3) for discharging the gas to be compressed from the side channel (30), the gas outlet opening (32) being in flow connection with the gas inlet opening (31) by way of the side channel (30), and a impeller (2) mounted for rotary drive in the housing (3), the impeller (2) having at least two impeller blades (1) disposed in the side channel, wherein at least one impeller blade (1) has a flow recess in its free edge region (47).

Description

Background of the invention

Field of the Invention

The invention relates to a side channel compressor for compressing a gas. The invention, therefore, relates to a working machine for compressing gases, such as air or technical gases.

Background Technique

The operation of the side channel compressor results in a wide spectrum of sound. In conventional side channel compressors, the tonal components of sound occur at certain frequencies of the side channel compressor, which are extremely annoying if they differ from the broadband sound spectrum by more than 7 dB.

US 2005/0207883 A1, which is considered as the closest prior art of the subject matter of claim 1, describes a blower having a resonant ring. A plurality of driving vanes extends from the resonant ring. A plurality of resonant cavities is embedded in the resonant ring. Each resonant cavity has a recess and a mouth that is open towards a gap between two adjacent driving vanes. During operation, the blower is very loud.

Summary of the invention

The object of the invention is to provide a side channel compressor that ensures particularly quiet operation. This object is achieved by a side channel compressor to compress a gas, the side channel compressor comprising a housing; a side channel located in the housing to compress a gas; a gas inlet opening formed in the housing, which is in flow connection with the side channel to introduce a gas to be compressed; a gas outlet opening formed in the housing, to discharge the gas to be compressed from the side channel, the gas outlet opening being fluidly connected to the gas inlet opening through the side channel; and an impeller that is mounted for rotary actuation in the housing and which has at least two driving vanes arranged in the side channel, in which at least one driving wall has at least one flow recess in its free edge region, wherein at least one flow recess is a flow groove having a substantially rectangular cross-section, in which only 30 to 70% of all driving vanes are grooved. The essence of the invention is that at least one flow recess is provided in the free edge region of at least one driving vane of the side channel compressor. The free edge region is the region that is located in the side channel and that may be surrounded by the gas to be compressed. The at least one flow recess or the amount of gas flowing through this flow recess, respectively, reduces the gas turbulence structures and / or the periodic gas flow structures that occur on the rear side of the vanes driving This ensures a particularly quiet operation of the side channel compressor.

The following is a detailed description of the various preferred embodiments of the invention by the accompanying drawings.

Brief description of the drawings

Figure 1 shows a side view of a side channel compressor and a transmission flange mounted on

the side channel compressor, the Figure showing a partial longitudinal sectional view of the

side channel compressor;

Figure 2 shows a front elevation view of the side channel compressor shown in Figure 1;

Figure 3 shows a front elevation view of the side channel compressor shown in Figure 2, with its housing cover removed;

Figure 4 shows a schematic view of a non-inventive impeller according to a first embodiment of a side channel compressor;

Figure 5 shows a substantially rear view of a driver impeller vane shown in Figure 4;

Figure 6 shows a schematic view of a non-inventive impeller according to a second embodiment;

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Figure 7 shows a substantially rear view of a driver impeller vane shown in Figure 6;

Figure 8 shows a schematic view of a non-inventive impeller according to a third embodiment;

Figure 9 shows a substantially rear view of a driver impeller vane shown in Figure 8;

Figure 10 shows a schematic view of a non-inventive impeller according to a fourth embodiment;

Figure 11 shows a substantially rear view of a driver impeller vane shown in Figure 10;

Figure 12 shows a schematic view of a non-inventive impeller according to a fifth embodiment;

Figure 13 shows a substantially rear view of a driver impeller vane shown in Figure 12;

Figure 14 shows a schematic view of a non-inventive impeller according to a sixth embodiment;

Figure 15 shows a substantially rear view of a driver impeller vane shown in Figure 14;

Figure 16 shows a schematic view of a non-inventive impeller according to a seventh embodiment;

Figure 17 shows a substantially rear view of a driver impeller vane shown in Figure 16; Y

Figure 18 shows a schematic view of an impeller of the invention according to an eighth embodiment.

Description of preferred embodiments

A side channel compressor shown in Figures 1 to 3 for compressing a gas comprises an impeller 2 that is provided with driving vanes 1 and is mounted in a housing 3 to rotate about a horizontal central longitudinal axis 4. A conventional actuator 6 serves to rotatably drive the impeller 2 in the direction of the arrow 5. The gas is thus transported through the housing 3 also in the direction of the arrow 5.

The housing 3 comprises a housing body 7 and a removable housing cover 8 which are joined together in accordance with Figures 1 and 2, so that they enclose the impeller 2 comprising the driving vanes 1, which is operable for rotation and which It is arranged on a drive shaft 9 for joint rotation therewith.

The impeller 2 is provided with a single vane ring and is designed as a disk. The impeller 2 comprises an internal impeller hub 10 with a caliber of the central circular hub 11. The impeller hub 10 is formed by an inner hub foot 12 that radially outlines the caliber of the hub 11 and by a radial circular hub washer 13 adjacent to the foot of the hub 12. In addition, the impeller 2 comprises a radial external support ring 14 adjacent to the outside of the washer of the hub 13 and which overlaps with both sides of said washer of the hub 13 in the direction of the central longitudinal axis 4. The ring of the support 14 carries a multitude of radially projecting vanes 1, which are distributed in the circumferential direction. In this embodiment, a total of 52 individual drive vanes 1 are provided, which are preferably arranged equidistant, so that they have an angular distance from each other, relative to the central longitudinal axis 4, which is approximately 7 °. In this way, 6 or 7 driving vanes 1 are arranged at every 45 °. The foot of the hub 12, the washer of the hub 13 and the support ring 14 form an integral casting.

The terms "axial" and "radial" used herein are relative to the central longitudinal axis 4. The terms "internal" and "external" are also relative to the central longitudinal axis 4. The term "internal" means that an internal region is closer to the central longitudinal axis 4 than an external region.

The caliper of the central hub 11 can receive the drive shaft 9. A conventional parallel key connection is provided between the drive shaft 9 and the foot of the hub 12, so that it transmits the torque generated by the drive shaft 9 to impeller hub 10 to rotate impeller 2.

The body of the housing 7 comprises a central hub part 15 that delimits radially and axially a space 16 for partially receiving the hub. A caliber of the central shaft 17 passes through the hub portion 15 and opens to the partial receiving space 16 of the hub. An annular side wall 18 is contiguous to the hub portion 15, said annular side wall 18 extending radially outwardly from the hub portion 15. A circumferential channel part 19 is contiguous to the outside of the side wall 18. The hub portion 15, the side wall 18 and the channel part 19 form an integral casting, which forms the body of the housing 7. The rod bands 20, which extend as radii, are provided outside the body of the housing. housing 7, which considerably increases the stability of the housing body 7. In addition, the screw heads 21 project radially outwardly from the side wall 18.

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The housing cover 8 is secured to the housing body 7 by means of several connecting screws 22, and comprises a central hub part 23 that radially and axially delimits a partial reception space 24 of the hub. An annular side wall 25, which extends radially outwardly, is contiguous to the hub part 23. A circumferential channel part 26 is fixed to the outside of the side wall 25. A rolling bearing 27 for the drive shaft 9 it is arranged in the hub part 23. The hub part 23, the side wall 25 and the channel part 26 form an integral casting, which forms the housing cover 8. Similarly, the rod bands 28, which are they extend as radii, they also project from the outside of the side wall 25, to reinforce the housing cover 8.

The housing body 7 and the housing cover 8 are joined together, so that the two partial reception spaces 16, 24 of the cube define a reception space 29 of the cube between them, and the two channel parts 19, 26 define a side channel 30 between them, for gas compression. The two side walls 18, 25 are parallel but spaced apart. The lateral channel 30, which is spaced from the central longitudinal axis 4, extends annularly around the central longitudinal axis 4 and is delimited by the channel parts 19, 26.

An opening 31 for axial gas inlet projecting in the side channel 30 is formed at the bottom of the housing cover 8. An opening 32 for axial gas outlet is further provided at the bottom of the housing cover, which It is in flow connection with the side channel 30, as well as adjacent to the opening 31 for gas inlet. A projected gas inlet connector 33 is connected to the opening 31 for gas inlet, while a gas outlet connector 34, which is projected in a similar manner, is connected to the opening 32 for gas outlet. An interceptor 35 is disposed in the side channel 30, between the opening 31 for gas inlet and the opening 32 for gas outlet.

The foot of the hub 12 of the impeller 2 is arranged in the receiving space 29 of the hub, defined by the hub portions 15, 23, passing the drive shaft 9 through the gauge of the hub 17. The drive shaft 9 is provided of a free radial bearing 36 at its end, which is mounted for rotation in the rolling element bearing 27 in the housing cover 8. The rolling element bearing 27 is provided with an inner ring 37 connected to the radial bearing 36 and a outer ring 38 connected to the housing cover 8, the rings being separated by rolling elements - in the form of rolling balls 39 - arranged between them. The inner ring 37 is compressed on the radial bearing 36 for joint rotation therewith, while the outer ring 38 is fixed to the housing cover 8 in a non-rotating manner. The washer of the impeller hub 13 extends radially outwardly from the foot of the hub 12, between the spaced apart side walls 18, 25 of the housing 3. The support ring 14 and the impeller vanes 1 are located in the circumferential lateral channel 30. A certain part of the foot of the support ring 14 is located in a recess 40 open outwardly, which is formed in the channel portions 19, 26, near the side walls 18, 25.

The side channel 30 has a free cross-sectional area that is available to transport the gas, and is approximately perpendicular to the arrow 5. Said cross-sectional area narrows from an area of the cross-section AE in the opening 31 for entry of gas to an area of the cross-section AA in the opening 32 for gas outlet, so that AA <AE. The side channel 30, however, may have a constant cross-sectional area as well.

The side channel 30 has a radial height S. The actuator 6 is an electric motor that is detachably connected to the outside of the housing body 7. To this end, various fastening screws are provided that are screwed into the screw heads 21 in the housing body 7.

To ensure that the unit formed by the side channel compressor and the actuator 6 is securely installed, the support feet 41 are formed in the lower part of the side channel compressor, while the support feet 43 are formed in the lower part of a support body 42 also, in which the support body 42 is connected to the housing body 7 by screws and carries the actuator 6.

A vertical plane E crosses the central longitudinal axis 4 and cuts with the side channel compressor in a vertically symmetrical manner, or centrally along the length, respectively.

The driving vanes 1 according to a first embodiment are now described in more detail by means of Figures 4 and 5. Each driving vane 1 is designed substantially as a plate, and has a substantially rectangular shape, with a corresponding contour. The driving vanes 1 are designed identically and symmetrically with respect to a plane of symmetry X, which is oriented perpendicular to the vertical plane E, and which crosses the center of the washer of the hub 13. Each driving vane 1 additionally has an edge that it is composed of a radially external edge region 45, a radially internal edge region 46 opposite it, and lateral edge regions 47, which interconnect the external and internal edge regions. The inner edge region 46 is in direct connection with the support ring 14 and can also be considered as the foot area of the driving vane 1, while the entire edge region 45 - which can be considered as the front area of the vane impeller 1 - is located completely in the lateral channel 30, and is oriented substantially parallel to the central longitudinal axis 4. The lateral edge regions 47 are substantially parallel to each other, and extend substantially radially outwardly from the internal edge region 46. Edge regions 45 and 47 are free, in other words, there are no elements adjacent to them. The inner edge region 46, on the other hand, is not free, since it is adjacent to the support ring 14. The edge regions 45, 46, 47 define a front surface 48 oriented in the direction of the arrow 5, and a rear surface 49 opposite thereto, therefore oriented in the opposite direction of the arrow 5. Each driving vane 1 additionally comprises an inner edge portion 50 contiguous with the inner edge region 46, and the outer edge portion 51 is contiguous with the outer edge region 45. The inner edge portion 50 extends radially outwardly from the inner edge region 46, while the outer edge portion 51 is slightly inclined forward in the direction of arrow 5, relative to to the inner edge portion 50 for flow reasons. The outer edge portion 51 is also reduced in thickness towards the outer edge region 45 when viewed in the circumferential direction.

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The distance between the outer edge region 45 and the inner edge region 46 defines a radial height H of a driving vane 1, assuming the radial height H of the inner edge portion 50, preferably between 55% and 75% of the radial height H. The radial height H is present near the lateral edge regions 47. Additionally, each driving vane 1 has an axial width B which is defined by the distances between the opposite edge regions 47.

The radial height H of the driving vane 1 is smaller than the radial depth S of the side channel 30. The radial height H is between about 50% and 75%, preferably up to about 60% of the radial depth S of the side channel 30. Furthermore, the axial width B of the driving vane 1 is always considerably smaller than the corresponding axial width of the side channel 30.

In this embodiment, the side edge regions 47 of the driving vane 1 are in each case additionally equipped with a reduction groove 52, which has a substantially rectangular cross-section, said reduction groove 52 being axially open outwardly, and is parallel to the outer edge region 45. These reduction grooves 52 are not shown in Figures 1 to 3. Each reduction groove 52 opens to the corresponding front surface 48 and the rear surface 49 of a driving vane 1, passing from this way along the entire outer side face of the driving vane 1. The opposite reduction grooves 52 are at a common level in the inner edge part 50. They are located in the lower half of the inner edge part 50, at a distance from the inner edge region 46, each of the reduction grooves having a radial height A which is between about 5% and 20%, preferably between 10% and 15% of the radial height H of a driving vane 1. The axial depth T of a reduction groove 52 is between about 2% and 12%, preferably between 5% and 9% of the axial width B of a driving paddle 1.

The following is a description of a non-inventive side channel compressor. The drive shaft 9 is rotated about the central longitudinal axis 4 in the direction of the arrow 5 by the actuator 6. Since it is coupled to the drive shaft 9 for joint rotation therewith, the impeller 2 comprising the driving vanes 1, therefore, also begins to rotate in the direction of the arrow 5. When passing near the opening 31 for gas inlet, the driving vanes 1 direct the gas to be compressed to the side channel 30, through the connector 33 of gas inlet and opening 31 for gas inlet. The gas located in the side channel 30 is accelerated, by means of the driving vanes 1, in the direction of the arrow 5, which can therefore also be referred to as a transport arrow. The front surfaces 48 of the driving vanes 1 are facing forward, in the direction of the arrow 5, and serve to transport the gas located in the side channel 30. During transport, the gas is practically trapped in the cells 44, which are internally delimited by the support ring 14 and adjacent driving vanes 1 in the circumferential direction. A cell 44 is defined in particular by the front surface 48 of a driving vane 1 and the rear surface 49 of a driving vane disposed adjacent thereto. The edge regions 45, 47 are free, thus allowing gas to flow through, or pass through, respectively.

Due to the reduction grooves 52, the respective surface area of the front surfaces 48 and the rear surfaces 49 of the driving vanes 1 is smaller than that of the conventional non-slotted driving vanes. The reduction slots 52 form flow channels, which allow a part of the gas to pass from one cell to another cell 44 below, which is located in the opposite direction of the arrow 5. The reduction slots 52, in this way, they also act as lateral flow slots through which a part of the gas can flow. These reduction slots 52, or the amount of gas flowing through these reduction slots 52, respectively, lead to a reduction of the gas turbulence structures on the rear side of the driving vanes 1. This reduces, in particular, , the magnitude and intensity of the gas turbulence structures in the side channel 30 and, consequently, leads to a reduction in pressure variations. The operating noise of the side channel compressor is also reduced. At the end of the circulation zone, the compressed gas is discharged from the side channel 30 through the gas outlet opening 32 and the gas outlet connector 34 via the driving vanes 1. The angular path covered by the gas in The side channel compressor is approximately 300º. The interceptor prevents the gas transported by the impeller 2 from being carried from the opening 32 for gas outlet to the opening 31 for gas inlet in the side channel 30.

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The following is a description of a non-inventive embodiment by means of Figures 6 and 7. The identical parts are denoted with the same reference numbers as in the first embodiment shown in Figures 4 and 5, a description to which reference is made. Parts that are of different design, but have the same function, are denoted with the same reference numbers, with one behind. The impeller 2a shown in Figure 6 differs from the impeller 1 shown in Figure 4 with respect to its driving vanes 1a, which are again symmetrical with respect to the plane of symmetry X. Unlike the driving vanes 1 according to Figures 4 and 5, the driving vanes 1a are provided with two identical reduction grooves 52, spaced apart, in each edge region 47a, said reduction grooves 52 being parallel to each other and to the outer edge region 45. The reduction grooves 52 in each They are located in the inner edge part 50 and are arranged one above the other. These pass through the entire driving vane 1 again, thus forming practically flow channels. The lower reduction groove 52 is disposed at a distance from the lower edge region 46 while the upper reduction groove 52 is disposed at a distance from the edge portion 51. With regard to the design, dimension and function of the reduction slots 52, reference is made to the aforementioned embodiment. In comparison with the aforementioned embodiment, that is, in comparison with the driving vanes 1 according to the first embodiment, the surfaces 48a, 49a of the driving vanes 1a are even smaller, and due to the duplication of the reduction grooves 52, The amount of gas can flow approximately twice from cell 44 to cell 44. The gas turbulence structures on the rear side are further reduced.

The following is a description of a third non-inventive embodiment by means of Figures 8 and 9. Identical parts are denoted with the same reference numbers as in the second embodiment shown in Figures 6 and 7, a description to which reference is made. Parts that are of different design, but have the same function, are denoted by the same reference numbers, with a b behind. Unlike the aforementioned embodiment shown in Figures 6 and 7, this embodiment is provided with a reduction groove 52 in the outer edge portion 51b as well. Each edge region 47b is provided with a total of three identical reduction grooves 52 which, in each case, are spaced apart. They are parallel to each other and with respect to the outer edge region 45. The upper reduction groove 52 in the edge portion 51b is disposed at a distance from the outer edge region 45. The reduction grooves 52 are arranged some above the others at identical distances from each other. The driving vanes 1b are again symmetrical with respect to the plane of symmetry X. With regard to the dimensioning, design and function of the reduction grooves 52, reference is made to the aforementioned embodiment. In comparison with the second embodiment, the turbulence structures on the rear side are further reduced since the additional reduction grooves 52 make the surfaces 48b, 49b even smaller, thus allowing more gas to flow through the reduction slots 52.

The following is a description of a fourth non-inventive embodiment of the invention by means of Figures 10 and 11. Identical parts are denoted with the same reference numbers as in the third embodiment shown in Figures 8 and 9, description to which refers. Parts that are of different design, but have the same function, are denoted with the same reference numbers, with a c behind. The only difference with the third embodiment according to Figures 8 and 9 is that the reduction slots 52c have a semi-circular cross-section instead of a rectangular one. Again, they are open axially outward and pass through all the driving vanes 1c. They are arranged one above the other, and have a maximum depth that is equal to the depth T. Their maximum external height is approximately equal to the height A. With respect to the position and function of the reduction slots 52c, it is refers to the third embodiment. In this embodiment, the driving vanes 1c are subjected to a particularly low notch effect. The semi-circular reduction slots 52c are also suitable for the first and second embodiments.

The following is a description of a fifth non-inventive embodiment by means of Figures 12 and 13. Identical parts are denoted with the same reference numbers as in the first embodiment shown in Figures 4 and 5, a description to which reference is made. Parts that are of different design, but have the same function, are denoted with the same reference numbers, with a d behind. Unlike the first embodiment shown in Figures 4 and 5, the side edge regions 47d are not provided with reduction grooves. Instead, the outer edge region 45d is provided with four identical reduction slots 52, spaced, which pass through the entire driving vane 1d and are arranged close to each other. In this embodiment, the reduction grooves 52, which form the flow channels, are only located at the outer edge portion 51, and have a radial depth that is substantially equal to the depth T. Their width is also substantially equal to the height A, so that the cross-sectional area of a reduction groove 52 in this manner is equal to the cross-sectional area of a reduction groove 52 shown in Figures 4 and 5. The reduction grooves 52 have a section transverse rectangular and are open radially outward. They have an identical distance from each other. The driving vanes 1d are designed symmetrically with respect to the X plane. This design reduces the gas turbulence structures also on the rear side. As regards the dimensioning and shape of the reduction grooves 52, reference is made to the first embodiment. Instead of the four reduction slots 52, only one central reduction slot 52 can be provided. However, each driving vane 1d can also be provided with two, three even more reduction slots 52, which should then be arranged preferably symmetric Instead of the rectangular shape shown here, other shapes are also applicable, such as a semi-circular shape.

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The following is a description of a sixth non-inventive embodiment by means of Figures 14 and 15. Identical parts are denoted with the same reference numbers as in the third or fifth embodiments, respectively, shown in Figures 8 and 9, as well as in Figures 12 and 13, description to which reference is made. Parts that are of different design, but have the same function, are denoted with the same reference numbers, with an e behind. This impeller 2e has driving vanes 1e which are substantially a combination of the driving vanes 1b and 1d shown in Figures 8, 9 and 12, 13. In this embodiment, each driving vane 1e has three spacing slots 52 spaced apart by on top of the others in each side edge region 47b, and four spaced reduction grooves 52, arranged in succession in the radial outer edge region 45d of the driving vane. With regard to the dimensioning, position and shape of the reduction grooves 52, reference is made to the first, third and fifth embodiments. In this embodiment, each of the free edge regions 45d, 47b is therefore provided with grooves, which results in a particularly low turbulence structure on the rear side, since a particularly high number of reduction slots 52 and surfaces 48e, 49e are particularly small. The driving vanes 1e are again symmetrical with respect to the plane of symmetry X. Alternatively, the semi-circular reduction grooves 52c are also applicable in this embodiment. Additionally, each of the edge regions 45d and / or 47b may be provided with a different number of reduction grooves 52.

An axially lateral and / or radially external groove of the driving vanes reduces the front and rear surfaces thereof forming flow channels, thereby reducing the turbulence structures on the rear side. The reduction slots can be of any desired shape. For this purpose, each driving vane is provided with at least one reduction groove. Each of the lateral edge regions and / or the radially external edge regions may be provided with any desired number of grooves. The driving vane itself can also be provided with reduction grooves of different shapes. Each lateral edge region and / or each external edge region is provided with at least one reduction groove, being able to randomly select the actual number thereof in the respective edge regions, and may be different from one edge region to the next. A symmetrical design of the driving vanes or a symmetrical arrangement of the reduction slots respectively is preferred.

As a non-inventive alternative to the grooves described, the lateral edge regions may also be bevelled, in other words, they may have the vane edges folded and / or the radially external edge regions may also be beveled. These bezels form flow recesses again, which reduce the front and / or rear surfaces of the driving vanes, so that the turbulence structures on the rear side are minimized. The lateral flow recesses may be oriented so that the driving vanes become larger or smaller from their front surfaces to their rear surfaces. The driving vanes or the lateral edge regions, respectively, can also converge upwards or radially outwards, respectively, so that the outer edge portion has a substantially trapezoidal shape, for example. In that case, the flow recesses are thus provided, both radially and laterally.

The following is a description of a seventh non-inventive embodiment by means of Figures 16 and 17. The identical parts are denoted with the same reference numbers as in the first embodiment, a description to which reference is made. Parts that are of different design, but have the same function, are denoted with the same reference numbers, with an f behind. In all the aforementioned embodiments, the impeller 2 has a single vane ring. In this embodiment, on the other hand, the impeller 2f is configured as a double vane ring with another external support ring 53, which delimits the cells 44 radially outward, and which is contiguous with the outer edge region 45f of the vanes 1f drives. On the other hand, there are no major differences compared to the first embodiment. The individual driving vanes 2f, again, are symmetrical with respect to the plane of symmetry X. As in the first embodiment, each edge region 47f of this embodiment is provided with a reduction groove 52. The reduction grooves 52 are adjacent to the corresponding edge region 46f. With regard to the shape, dimensioning and position of said reduction grooves 52, reference is made to the first embodiment. According to alternative embodiments, each of the side edge regions 47f is further provided with a reduction groove 52. Alternatively, the reduction grooves 52, again, are designed to have a different cross-section, for example, semi -circular. Again, other recesses, such as bevels, are also conceivable in the edge regions 47f.

The following is a description of an eighth embodiment of the invention by Figure 18. Identical parts are denoted with the same reference numbers as in the embodiment shown in Figures 4 and 5, a description to which reference is made. Unlike the first embodiment, not all the driving vanes 1 of this embodiment are grooved in the lateral edge regions 47, but only from 30% to 70%, preferably from 40% to 60% of all the driving vanes. In this embodiment, the driving vanes 1 with reduction slots 52 according to the first embodiment are arranged between the driving vanes without reduction slots. Slotted driving vanes 1 are arranged randomly, that is, stochastically. As shown in the upper part of Figure 18, three regular impeller vanes are provided, ie not slotted, between two slotted vane vanes 1. On the upper side faces on one side, only two regular impeller vanes are provided between two Slotted drive vanes 1. However, it is also conceivable to have two slotted drive vanes 1 directly behind each other. In this embodiment, the reduction slots 52 act as reduction slots to reduce periodic flow structures. This prevents the formation of harmonic flow structures, thus ensuring a particularly quiet operation of the side channel compressor. Again, the gas turbulence structures on the rear side are also reduced.

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Instead of the driving vanes 1 described here in accordance with the embodiment shown in Figures 4 and 5, the other driving vanes mentioned above are also applicable. Also, various driving vanes different from the aforementioned embodiments can be provided in the impeller itself. Sequential repetitions are possible. Alternatively, identical grooved vane vanes can be provided several times in a row. The sequence, in this way, is completely random. What is essential is that the driving vanes are designed differently, for example in terms of their shape and / or size. The driving vanes can also differ only in height and / or width. Preferably, they are arranged equidistant.

The side channel compressor may comprise at least one stationary projection to engage with the at least one flow recess or reduction groove 52, 52c. In contrast to the at least one mobile flow recess or reduction groove 52, 52c, the at least one projection is motionless.

The interceptor 35 for the impeller 2, 2a, 2b, 2c, 2e, 2f can have at least one projection that projects towards the impeller 2, 2a, 2b, 2c, 2e, 2f and can be engaged with at least one flow recess or reduction groove 52, 52c on the side edges 47, 47a, 47b, 47c, 47f of the driving vanes 1, 1a, 1b, 1c, 1e, 1f. A projection of the interceptor 35 is provided for each flow recess or reduction slot 52, 52c. The interceptor 35 for the impeller 2 has a projection. The interceptor 35 for the impeller 2a has two different projections. Interceptors 35 for impellers 2b, 2c and 2e have three different projections. The interceptor for impeller 2f has a projection. The size and design of the projections are adapted to the size and design of the flow recesses or reduction slots 52, 52c. There is a small play between the at least one projection and at least one flow recess or reduction groove 52, 52c. The at least one projection counteracts the release of pressure.

According to a further embodiment, there is at least one projection in the housing 3 that projects towards the impeller 2, 2a, 2b, 2c, 2d, 2e, 2f and can be engaged with the at least one flow recess or reduction groove 52, 52c. The at least one projection can be engaged with the flow recesses or reduction grooves 52, 52c at the side edges 47, 47a, 47b, 47c, 47f and / or at the front edges 45, 45d. The size and design of the at least one projection are adapted to the size and design of the flow recesses or reduction slots 52, 52c.

The at least one projection may have an elongated curved shape, which is concentric with respect to the longitudinal axis.

Four.

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Claims (12)

one.

 A side channel compressor for compressing a gas comprising:

a) a housing (3), b) a side channel (30) located in the housing (3) to compress a gas, c) an opening (31) for gas inlet, formed in the housing (3), which is in flow connection with the side channel (30) to introduce a gas to be compressed, d) an opening (32) for gas outlet formed in the housing (3) to discharge the gas to be compressed from the side channel (30), the opening (32) for gas outlet being in flow connection with the opening (31) for gas inlet through the side channel (30) and e) an impeller (2; 2a, 2b; 2c; 2d; 2e; 2f) which is mounted for rotary drive in the housing (3) and which has at least two driving vanes (1; 1a; 1c; 1d; 1e; 1f) arranged in the side channel (30), f) in which at least a driving vane (1, 1a, 1b; 1c; 1d; 1e; 1f) has at least one flow recess (52, 52c) in its free edge region (45d; 47; 47a; 47b; 47c; 47f); the compressor being characterized in that at least one flow recess (52; 52c) is a flow groove having a substantially rectangular cross section, and that only 30% to 70% of all driving vanes (1) are grooved .

2.

 A side channel compressor according to claim 1, wherein each driving vane (1, 1a, 1b; 1c; 1d; 1e; 1f) has side edges (47; 47a; 47b; 47c; 47d; 47f), wherein the lateral edges (47; 47a; 47b; 47c; 47d; 47f) are provided with flow recesses (52, 52c), so as to reduce gas turbulence structures.

3.

 A side channel compressor according to claim 2, wherein each side edge (47; 47a; 47b; 47c; 47f) is provided with at least one flow recess (52, 52c).

Four.

 A side channel compressor according to claim 1, wherein each driving vane (1, 1a, 1b; 1c; 1d; 1e; 1f) has a leading edge (45; 45d), the leading edges (45d being provided) ) of flow recesses (52; 52c) to reduce gas turbulence structures.

5.

 A side channel compressor according to claim 1, wherein at least two driving vanes (1, 1a, 1b; 1c; 1d; 1e; 1f) differ from each other to reduce periodic flow structures.

6.

 A side channel compressor according to claim 5, wherein each driving vane (1, 1a, 1b; 1c; 1d; 1e; 1f) has a leading edge (45 d), in which at least two driving vanes (1, 1a, 1b; 1c; 1d; 1e; 1f) differ in terms of their leading edges (45; 45d).

7.

 A side channel compressor according to claim 6, wherein the leading edges (45; 45d) differ in terms of the flow recesses (52; 52c).

8.

 A side channel compressor according to claim 5, wherein the driving vanes (1, 1a, 1b; 1c, 1d, 1e; ...; 1f) have side edges (47; 47a; 47b; 47c; 47d ; 47f), in which at least two driving vanes (1, 1a, 1b; 1c; 1d; 1e; 1f) differ in terms of their lateral edges (47; 47a; 47b; 47c; 47d; 47f).

9.

 A side channel compressor according to claim 8, wherein the side edges (47; 47a; 47b; 47c; 47d; 47f) differ in terms of the flow recesses (52; 52c).

10.

 A side channel compressor according to claim 5, wherein the driving vanes differ in terms of their size.

eleven.

 A side channel compressor according to claim 5, wherein the different driving vanes (1, 1a, 1b; 1c; 1d; 1e; 1f) are arranged in a random sequence.

12.

 A side channel compressor according to claim 1, comprising at least one stationary projection to engage with the at least one flow recess (52, 52c).